Automatic multiple speed transmission



Oct. 14, 1958 D. L. MOUNT AUTOMATIC MULTIPLE SPEED TRANSMISSION Filed Aug. 10,8195@ 5 Sheets-Sheet l Oct. 14, 1958 Filed Aug. l0. 1956 D. l.. MOUNT 2,855,788

AUTOMATIC MULTIPLE SPEED TRANSMISSION 3 Sheets-Sheet 2 ATTORNEYS.

Oct. 14, 1958 n.1.. MoUNT AUTOMATIC MULTIPLE SPEED TRANSMISSION United States; Patent i 2,855,788 AUTOMATIC MULTIPLE SPEED TRANSMISSION l Y Donald L. Mount, Memphis, Mo. l Application August 10, 1956, Serial No. 604,586. 16 claims. (ci. 74-368) This invention relates to an automatic multiple speed transmission designed particularly for economical manui `loss of momentum caused by declutching between gear shifts sometimes results in stopping of the tractor.

One object of my present invention therefore is to provide a multiple speed transmission in which there is a clutch for each speed range, and in going from one speed range to a higher one declutching of the lower speed gears is not necessary due to an overrun clutch connection between the lower speed gears and the output shaft of the transmission. Similarly there are over run` connections between all other gears and the output shaft where required to permit a higher'speed clutch to take over and operate the tractor' or the" like at the f `higher speed without first declutching the-lower speed gear. i f

Another object is to provide a power transmission in which various gears thereof remain in mesh, and clutches remain engaged in such manner that shift from one gear 'arrangement to a higher one is accomplished while the power is constantly connected through the transmission to Athe driven shaft without the necessity of having to throw out an engine clutch between gear shifts, and likeyWise in down-shifting there is no declutching when shifting from any gear to a lower gear. Still another object is to provide a transmission with a gearing arrangement that permits operation in different ranges so that the number of gear changes may be doubled by a simple set of gears that shift from one range to the other. For instance, if the transmission is designed for four speeds, a gear shift from one range to the other can increase the number of speeds to eight except where one of the speeds is direct drive which would be operable in either range thus reducing the number of speed shifts to seven.

A further object is to provide a transmission which has as one of its speeds an overdrive operable so that overdrive in relation to direct drive is had in one of` the ranges but a different and lower gear in relation'to direct drive is had in the other range, thus permitting a relatively great total range from the lowest speed to overdrive with relatively small speed change steps.

'f Still a further object is to provide a convenient control means for securing the various speeds both forward :and reverse, two speeds in reverse being had by reason -of the two ranges of the transmission without undue complication of the reverse gearing.

An additional object is to provide free-wheeling or v vention;

2 coasting prevention clutches as part of my transmission and a selective control therefore to render them operable or inoperable as desired `so that the transmission can be thus operated with or without the free-wheeling prevention feature.

Another additional object is to provide simplified and/or modified forms of my transmission utilizing some or all of its features but with fewer speed changes possible.

With these and other objects in view, my invention consists in the construction, ,arrangement and combination of the various parts of my automatic multiple speed transmission, whereby the objects above contemplated are attained, as hereinafter more fully set forth, pointed out in my claims and illustrated in detail on the accompanying drawings, wherein:v

Fig. 1 is a vertical sectional view through an automatic multiple speed transmission embodying my present in- Fig. Z is an end elevation thereof showing a control handle and indicating dial arrangement;

Fig. 3 is a vertical sectional view on the line 3-3 of Fig. l showing friction and overrun clutch operating details, Fig, lkbeing taken on the line 1-1 of Fig. 3; Fig. 4 is a vertical sectional view on the line 4-4 of Fig. 1 showing particularly a reversing gear and a clutch therefor; y n

Fig.,r 5 is a vertical sectional view on the line 5`5 of Fig. l;

Fig. 6 is a vertical sectional view similar to the bracketed portion of Fig. 1 which is indicated (6) and shows modied details substituted for the bracketed portion;

Fig. 7 is another modification of the bracketed portion of Fig. l indicated (7) and shows modified details substituted for the bracketed portion;

Fig. 8 is a vertical sectional view through still another modified form of my `transmission showing a comparatively simple form having low and direct drive only; and Figs. 9 and l0 are similar views of modified portions of Fig. 8 showing different positions possible for an overv14 in the form of a sleeve around the shaft 12. This sleeve is, of course, connected to traction wheels or the like in the usual manner. A countershaft 16 is also journalled in the housing 10. v

I provide a low gear sleeve 18 rotatable on the input shaft 12 and operatively connectible with it by a clutch C1 which in Fig.`1 is shown in the engaged or in position. A low primary gear 20 is secured thereto and meshes with a low secondary gear 22 rotatable on a sleeve 24 which in turn is rotatable on the countershaft 16. The sleeve 24 has a low gear ange 26 forming part of an overrun clutch, the overrun rollers of which are shown at 28. A similar overrun clutch with overdrive secondary gear 70 and overrun rollers 76 is `shown in Fig. 5, to which reference is made for the details of the overrun clutch 22-26-28 and others to be desecribed. In Fig. 5, however, there is no ange as the overrun rollers engage the sleeve 24 directly.

Details of the clutch C1 will now be described. This clutch consists of an input friction disc 30 splined to the shaft 12, a oating output disc 32, clutch springs 36 to normally engage the clutch, pivoted clutch levers 38 to disengage the clutch and carried by a clutch housing 34 constituting also an output disc, and a thrust bearing v40 engaging the clutch levers and adapted to be actuated by a clutch actuating arm 42 for disengaging the clutch.

clutch actuating rod`44 carries the clutch actuating arm 42 and is slidable in the housing 10, its end extending out of the right-hand endV of the housing for actuation by a` clutch control lever l80through cam mechanism as '4` shown in Fig. 4. The idler 94 rotates on a stud 96 extending `from 'the 4housing '10.

Mounted on the countershaft 16 between the low gear flange 26 and the reverse secondary gear 92 is a clutch willb-eilater described. The springs 36 normally "bias the 5 C5. A clutch actuating arm 97 is provided therefor and clutchtothe fin position and the rod 44 ytoward the is mounted on a clutch actuating rod 98 extending out lever 80. of the right-hand end of the housing 10. The extending Freely rotatable on the input shaft 12 is a middle rod ends 44, 56, 78 and 69 are-shown in Figure 3 adja- :primary ,gear 46 meshing with a middle secondary gear cent the top of thehousingl and the rod ends 66 and :48 on a sleeve 50 Awhichis rotatable on the sleeve 24. 10 98 to the right of the shaft 16, and the clutches they .The sleeve 24 has a middle gear flange 52 forming part operate are indicated. of an overrun clutch in relation to the middle secondary For actuating the clutch rods 44, 56, 66, 69, 78 and 98, 4gear 4S which clutchincludes overrun rollers v54. 4The I provide a clutch contrllever 80 having a cam plate middle .primary gear v'46 is adapted to be operatively 86 with appropriate-lbes-.SS to ."depress the ends of the :connected with ltheV input shaft n12 by a clutch C2, the 15 clutch actuating rods against the bias of springs in a pre- A-,const'ruction of which is similar to the clutch C1 and determined pattern as will be referred to in a chart heretherefore I have 'omitted reference numerals and will below. The springs just referred to are the clutch springs not repeat the description. NLikewise'l have omitted ref- 36 for each of y.the `clutches C1, C2, .C3` and C4, and erencenumbers on other clutches C3, C4 and'C7 of simsprings 95 .and`'99ffor .therods .66 and 98 respectively. ilar construction. A'The clutch'CZ has a clutch actuating 20 -ndicia isprovided on'the outside of the cam plate 86 arm k55 extending from a clutch actuating rod 56 which asshownin Fig. f2 to cooperate with an index 84 to in- -likewise extends out of the right-hand end of the housing dicate Vthe diierentspeed shifts of the transmission. The "1.0 in a manner Ysimilar tothe rod 44. indicia may'be identified as follows, reading counter- There is a iirst range gear connection between the clockwise around the dial: countershaft 16 and the output sleeve 14 comprising a 25 l@D Ovmdw, primary gear`58 and a secondary gear 60. There is also .D fDrectdrive a` second rangegear connection between these two shafts 5, 4 .3 2, I Pmgressiwly lowerspeed ranges (5 in au) comprislng aprlmary gearv62 and secondary gear 64. Therst'range gears are lower ratio than the second The following are all reverseasdistinguished frornforrangegears. A clutch C6 is provided for selectively 30 Ward:

clutching either "58 or 62 to the countershaft 16 and the l\i-l\eutral clutch is actuated by a clutch actuating arm 65 connected ,Rl-Reverse-.in rangel with aclutchlactua'ting rod 66 which also extends out of TR2-Reverse in rangeZ the nght`hand end of the housmg 10' Thefchartreferredttoabove isasffollows:

Dial Gear Range, Ratio kC E O1 C2 C3 C4 C5 C6 (Gears) 0D (6s-70) R2 (135) C4.. Tn In 0ut F 62-64 Direct) R2 `(100) 03-.--

In out F (s2-64 MID (46-4s) R2 (67) C2 ,In Out Out F 62-54 OD (6s-7o) R1 (54) C4 yIn In F 58-60 Lo(2o22) R2 (45) 01---- ln- 'out out Ontw F (s2-s4 MID (4641s) R1 (27) 02---- out-" out- F 58-60 (Figs. l and 2) 1 Lomo-22) R1 (1s) 01.--- In.... out--. A,Out 0ut F 58-60 N None R1 O None.. Out-" Out-.. Out". Out N 58-60 R1 RR1(90-94-92) R1 (13R) C1 In- 0u1; Out out-" R .5s-60 R2 R-R2(90-9492). R2 (33E) 01---. Out Outm Out R 62-64 A cltch C3 Sirn'ilarito 'the clutches C1 and C2 is In'thefabove chart 'the column lheadings may be identi- "provided'as a'direct connection between the input shaft fied as follows: 12 and the output sleeve 14 and when this clutch is en- Dial-The indicia reading on the cam plate 86 (Fig. 2). gaged direct drive is had which I refer to as D in a Gear-Tlie'gear ranges already referred to with R-Rl Tchart later on in my specification. This is direct drive 55 being reverse in range land `R-R2 being reverse in las distinguished from low gear and middle gear indicated range 2. 'in said-chart -as LO and MID respectively. There Range-Range l and range 2 are indicated for gear sets fis -also a higher'gear than D which I designate OD Sii-6i) and 62-64 respectively as designated under C6. lfor overdrive. For operating the clutch C3, a clutch Ratio-This is'the approximate actual speed ratio as actuating rod 69 has a clutch actuating arm 67 and the 60 between the input shaft 12 and the output shaft 14-(135) `rod extends out of theright-hand end of the housing lil. being a ratio ofV 135 to'v ltli'letc.4 and (13R) being a ratio of A. My overdrive geararrangement comprises an over- 13 to 100 in reverse, etc. -drive primary gear `68`1neshing with an overdrive sec- C E-The particular clutch engaged when operating ondary gear 70 o'n av sleeve 72 rotatable on the sleeve in forward speed. This involves clutches C1, C2, C3 and 24. 65 C4, none of which are engaged in neutral (N). ln re- Inthe overdrive-gear'arrangement, overrun rollers 76 verse, C5 is shifted from the position shown in Fig. l to lcact directly with the sleeve 24 to constitute with the the reverse position in engagement witi gear 92 instead of overdrive secondary gear 70, an overrun clutch drive gear 26 and the clutch C1 is then the contro-lling clutch. "'from the shaft 12 tothe sleeve 24. A clutch actuating Ci to C6 are the six clutches already described, and C-arm'77is providedfor the'clutch C4 and a clutch actu- '70 under Cl to C4 they are designated either In or Out ating ro'd'78 therefor extends-out of the right-hand end depending on whether they are in engagement or dis- "of the housing 10. engaged. Under CS, forward, neutral and reverse posi- The freverse gearing-for lmy transmission includes a tions are indicated F, yN and R, respectively. The clutch reverse primary gear"=90, a reverse secondary gear 92 C6 is either in the first range or the second range, and and-a :reverse idler I'geef-94. vThe arrangement is best 75 gears involved are indicated,

The positions of the clutches C1'to C6 in the above chart are secured by the proper positioning of the cam lobes 88 coacting with the clsrtch rods 44, 56, 66, 69, 78 and 98 shown in Fig. 3. Different arrangements, of course, can be provided but it is desirable to have a progressive speed change such as from a ratio of 18 to a ratio of 135 in the forward range (as in the ratio column of the above chart) on one side of neutral (N), and a ratio of 13 and then 33V in reverse on the other side of neutral.

Figs. 1 and 2 show the parts of .the transmission in middle speed and rst range position with a consequent set of conditions existing in the sixth horizontal column (underlined) of the above chart.

The operation of my transmission is such that (consid ering the seven speeds 1, 2, 3, 4, 5, D and OD under Dial of the above chart) when speed 1 is in eiect and C1 only is closed, the drive is from 12 through the elements 18, 20, 22, 28, 26, C5, 16, 58 and 6i) to 14. When speed 2 is in eiect, rC2 is also closed and the drive is from 12 through C2, 46, 48, 54, 52, 24, 16, 58 and 60 to 14, 22-26-28 overrunning because 46-48 is al higher ratio than Ztl- 22. Likewise', when C3 is closed for speed D, direct drive is had from 12 through C3 to 14 and the gears 46-48 are overrun so that both of the overrun clutches 22-26--28 and 48-52-54 overrun.

At speeds 3 and 5, the diierence from speeds l and 2 are merely in the range-range 2 lbeing used instead of lrange l.l At speed 4, the overdrive gears 68 and 70 and the overdrive clutch 24-70-76 are involved so that drive from 12 is through C4, 68, 70, 76, 24, 16, 58 and 60 to 14. Even though the overdrive gear is in operation the ratio is less than (100) (direct drive D) because of the low gear ratio between 58 and 60 at speed OD, range 2 is involved (gears 62 and 64 instead of 58 and 60).

In each of the progressively higher speeds from speed 1 to speed D, one, two or three of the overrun clutches overruns so that in speed 2 for instance the ratio (27), see chart above, takes over from the ratio (18) without any loss of power and likewise the gears involved in each higher ratio merely overrun the previous gears so that there is no loss of traction from neutral through speed D. In overdrive, however, due to the ratio of range 2 gears 62-64 being less than the ratio of overdrive gears 68-70, it is necessary to Ithrow clutch C3 out when clutch C4 is thrown in and the clutch rod 78 therefore is out of circumferential alignment with the clutch rods 44, 56 and 69 so that proper lobes 88 of the cam plate 86 may be provided to accomplish this. sition, C3 does not need to be out when C4 is in because gears 68-76 do not overrun range l gears 58-60.

The change from speed D to speed OD can be performed rapidly before momentum is lost in speed D butin any case if it is lost, then the speed can drop no' lower than speed 5 because clutch C2 is in when the clutch control lever 80 is in the speed OD position. In reducing speeds, likewise there is no loss of power between one speed and another as for instance, from speed D to speed 5, because clutch C2 is in and ready to take over as soon as clutch C3 is thrown out Thus there is a smooth application of power from the engine to the traction wheels both in up-shifting and down-shifting of the transmission.

Neutral (N) is had by throwing clutches C1, C2, C3 and C4 out and moving the clutch C5 to neutral (a centered position between clutching with the gear 26 and clutching with the gear 92). When C5 is clutched with 92, then of course I have reverse, and in two different ranges by selecting the gears 58-60 or 62-64 (with C1 operable as the controlling clutch in this case). The cam lobes S8 can be readily designed to secure the desired control pattern in laccordance with the above chart.

The overrunclutches will permit free wheeling when In the speed 4 po the output shaft 11 rotates faster than it is normally driven vwhen shifting into overdrive.

times it is undesirable, however, to permit free-wheeling and accordingly I provide a means to prevent such in the form of ratchet clutches RC1, RC2 and RC3. RC1 is so linked up with C2 that when C2 is out, RC1 is in and vice versa. Similarly, RC2 and RC3 are linked up with the clutches C4 and C3 respectively. The heights of the lobes 88 for the clutch rods 56, 78 and 69 are such that they do not permit RC1, RC2 and RC3 to engage,vbut higher lobes do permit such engagement. These higher lobes are indicated 89 on the" drawing (Fig. 1).

The plate 36 between the different speeds forward has large dots which indicate for instance, speed 1`with RC1 engaged so that ythe speeds 1, 2, 3, etc. are without free wheeling as afforded by operation of the ratchet clutches RC1, RC2 and RC3. The dot between l and 2 indicates a position where the speed is l but free wheeling is permitted because the ratchet clutches RC1, RC2 and RC3 are all disengaged. The ratchet clutches are such that they prevent rotation in one direction and this is the direction that the traction wheels would drive the countershaft 16 in the event of coasting so that coasting is prevented when the clutches are in operation.

The ratchet clutches RC1, RC2 and RC3 are provided with springs 91 for normally engaging them and are held out of engagement by arms 53, 79 and 71 extending from the clutch actuating rods 56, 78, and 69 for the respective ratchet clutches RC1, RC2 and RC3. The springs 91, however, are much weaker than the main clutch springs 36 of the clutches C2, C4 and C3.

T he ratchet clutch arrangement disclosed as tied in with the other clutches provides for disengagement of RC1 etc. for instance before C2 closes while C1 stays closed normally when shifting from speed l to speedV 2. The cam plate 86 when half way between speed 1 and speed 2 disengages all three ratchet clutches so that free wheeling is permitted and likewise at the dots between the other speeds from 2 to OD. By tying RC1 in with the operation of C2 and likewise RC2 and RC3 in with C4 and C3 respectively, the low, direct and overdrive gears producefa progressive throwout of the ratchet clutches to accomplish the desired results. a i

In Fig. 6 I show a modification wherein the clutch C3 is connected with the output shaft 14 by an overrun clutch comprising overrun rollers between a hub 102 of the shaft 14 and an extension sleeve 104 of the clutch C3 rather than'the direct or solid connection between C3 and 14 as in Fig. l. This allows for a straight-through progressive change of speed up and down without the possibility of losing torque between speed D and speed OD In that case the speed OD in the above chart may be modified to the extent that the clutch C3 is in rather than out thus making the cam lobing 8S somewhat simpler in construction.

In Fig. 7 I have shown a modification of Fig. l wherein a single clutch C7' is provided to take the place of clutches C2, C3 and C4. The clutch C7 is connected with the gears 46 and 68 of Fig. l whereas the gears 43 and 70 of Fig. 1 are replaced by gears 43a and 76a with a selective clutch connection C8 between these gears and the countershaft 16. The clutch C1 is for lirst and second speeds through the gears 26 and 22 while C7 is for direct speed.

In explaining Fig. 7 I have disregarded the range l and range 2 gearing 58-60 and 62-64 of Fig. l which could be provided or not as desired. The clutch C8 (and likewise the clutches CS and C6 of Fig. l) may be ratchet tooth type to prevent coasting or for easy engagement. They may be synchro-mesh type if desired. Synchromesh type would provide positive rather than ratchet clutch connections with the usual brakes on the revolving parts as provided in conventional synchro-mesh clutches and transmissions to brake the parts to the same speed to prevent clashing when shifting gears or clutches. The synchro-mesh type is illustrated for the clutch C8 in Fig. 7, the clutch teeth being of the square-jaw type rather than the ratchet type, and the clutch being provided with cone with a gear 118 that drives the clutch C10.

.substantially the same result.

`7 brakes .124 at each end tocoop'erate .with mating cones 11:26-and y128 :for the-gears 43a and 70a. Thecones 126 and128 are slidably andnon-rotatably pinned to the gears 48a and 70a as illustrated and are normally in the extended ypositions shown under the action of springs 130 behind them.

Also, in ,-Fig. 7 l-showclutch` levers 132 `and 134 for the respectivefclutches"C1 and ..C7. Use vof the clutch.C1 is optional as if thefshaft'zlZis directly connected .toa source of power, neutral,` firstspeed, secondspeed and direct drive can be had by the use of C7 only. The operation of Fig. 7 secures first 'speed (when -SCS is to the right) from 12 .throughnCL 20, 22, 28, 26, 16, C8, 70a and 68 tothe out- .putfsleeve 14. For second speed, C8 is moved to the .left whereupon the power from C1-goesthrough20, 22, 28, 26, .16, C8,.43a, 4,6, the housing of C7 and-6% to the output sleeve 14. To secure direct drive, it is merely necessary -to throw inthe clutch C7 for clutching it to the input shaft -12, -and the output sleeve 14 then rotates simultaneously with the shaft 12.

The form of my transmission shown in Figs. 8, 9 and 10 shows low speed and direct drive without free-wheeling prevention clutches. Friction clutches C9 and C10 are shown which are operated by a foot clutch lever 108 and a hand clutch lever 110 respectively. The housing for the transmission is shown at 10a, the input shaft at 12a and the output shaft at 14a. A gear 112 on a shaft 113 vdriven by the clutch C9 meshes with a gear 114 on a countershaft 120. A pinion 116 on the countershaft meshes Interposed between the gear 114 and the countershaft 120 is an over- Arun clutch, `the overrun rollers of which are indicated at .As shown in Fig. 9, a plaingear 114a is substituted for .the gear 114 of Fig. 8 and an overrun gear 116a for the .plain gear 116 of Fig. 8. The overrun clutch 122 is then associated with the gear 116a. This arrangement produces substantially the same result as that shown in Fig. S, and in Fig. l is another arrangement producing In other words, the overrun clutch 122 can be interposed anywhere between the y.gear 112 and the clutch C10. In Fig. 10 it is shown associated with a gear 115:1 in place of the gear 118 instead yof with either the gear 116g or 114 as in Figs. 9 and 8 respectively.

In the operation ofthe transmission shown in Fig. 8,

,assuming both clutches .C9 and C10 disengaged, engagement of clutch C9 will operate the output shaft 14a at a reduced speed relative to the input shaft 12a by reason of the step-down gearing 112114-116-113. When the clutch C is then thrown in, it will directly connect 14a to 113 so that they rotate as a unit and the overrun clutch 122 will then become operative to permit relative rotation of the gears without any driving effect because the higher speed o-f the gear 118 in direct drive causes overrunning of the countershaft 120 relative to the gear 114. Likewise in Figs. 9 and l0, the overrun clutch will operate similarly.

From the foregoing specification it is believed obvious that I have provided a transmission which accomplishes the objects contemplated. Changes may be made in the construction and arrangement of the parts thereof without departing from the real spirit and purpose of my invention. It is, therefore, my intention to cover by my claims any modified forms of structure or use of mechanical equivalents which may reasonably be included within their scope.

I claim as my invention:

l. In an automatic, multiple speed transmission of the character disclosed, an input shaft, an o-utput shaft, a countershaft, first gear connections from said input shaft to lsaid countershaft and second gear connections from said countershaft to said output shaft, a clutch connection between said input shaft and said first gear connec tions, an additional clutch connection betweensaid firstv gear .connections and said4 output shaftyanoverrun clutch onisaidscountershaft.operable 'between said first gear-:connections and said countershaft, and means Vto controlxsaid clutch connections.

2. A multiple speed transmission of the characterdisclosed comprising an input shaft, Van outputshaft, .a Acountershaft, low, middle and overdrive gear connections from said-input'shaft tosaid countershaft, a clutchfor each of 'said.low, middle andoverdrive gear connections, a .gear connection from said countershaft to said output shaft, a clutch for direct drive. from said input shaft to `said output shaft, interconnected means to control said .clutches for-said gear connections and said clutch for `direct drive, and an overrun clutch included in Veach of :said Alow, middle and overdrive gear connections to permit :progressive up-shifting and down-.shifting ofsaid .transmission without declutchingsaid output shaftrelative to said input shaft.

3. vIn a transmission of the character disclosed, 'an .input shaft, an output shaft, a countershaft, low, middle and overdrive gear connections from said input shaft to1said countershaft, a clutch for each of said low, middle and overdrive gear connections, a clutch for direct drive from said input shaft to said output shaft, interconnected means to progressively engage said clutches for said low, middle and overdrive gear connections and said clutch for :direct drive, and an overrun clutch included inleachfofsaid l'ow,

'middle and overdrive gear connections to provide -constant application of power from said input shaft to said output shaft during up-shifting and down-shifting of said transmission.

4. In an automatic transmissionV of theV character rdisclosed, an input shaft, an output shaft, .a .countershaft, low, middle and overdrive gear connections from said input shaft to said countershaft, a clutch foreach .of said low, middle and overdrive gear connections, a clutch for direct drive from said input shaft to said output shaft, means to control said clutches for said low, middle `and overdrive gear connections and said clutch for direct drive, an overrun clutch included in each of said low, .middle and overdrive gear connections to permit progressive upshifting and down-shifting of said transmission, a plurality of gear connections between said countershaft and said output shaft, and means for shifting said last gear connections to different ranges of relative speeds in the same direction between said two shafts.

5. A transmission comprising an input shaft, an output shaft, a countershaft, low, middle and overdrive gear connections from said input shaft to said countershaft, a clutch for each of said low, middle and overdrive gear connections, a clutch for direct drive from said input shaft to said output shaft, an overrun clutch included in each of said low, middle and overdrive gear connections to `permit progressive up-shifting and down-shifting of said transmission without declutching said output shaft relative to said input shaft, and two ranges of gear connections between said countershaft and said output shaft, both of said ranges being in the same direction.

6. A transmission comprising an input shaft, an output shaft, a countershaft, low, middle and overdrive gear connections from said input shaft to said countershaft, a clutch for each of said low, middle and overdrive gear connections, a clutch for direct drive from said input shaft to said output shaft, means to control said clutches for said low, middle and overdrive gear connections and said clutch for direct drive, a plurality of gear connections between said countershaft and said output shaft, and means for shifting said last gear connections to different .ranges of forward speeds of said output shaft relative to 9 to said output shaft, an overrun clutch included in each of said low, middle and overdrive gear connections, a reverse gear connection between said input shaft and said countershaft, and interconnected means operable to selectively render one of said low, middle and overdrive gear connections inoperative and said reverse gear connection operative or vice versa.

8. In 'a transmission of the character disclosed, an input shaft, an output shaft, a countershaft, a gear connection from said input shaft to said countershaft, a clutch for said gear connection, a clutch for direct drive from said first clutch to said output shaft, means to control s'aid clutch for said gear connection and said clutch for direct drive, an overrun clutch between said first clutch and said gear connection, a reverse gear connection between said input shaft and said countershaft, and interconnected means operable to selectively renderA said rst tion operative or vice versa.

9. In an automatic, multiple speed transmission of the character disclosed, an input shaft, an output shaft, a countershaft, low, middle and overdrive gear connections from said input shaft to said countershaft, 'a clutch for each Iof said low, middle and overdrive gear connections, a clutch for direct drive from said input shaft to said output shaft, an overrun clutch included in each of said low, middle and overdrive gear connections to permit progressive up-shifting and down-shifting of s'aid transmission without declutching said output shaft relative to said input shaft, and a free-wheeling prevention clutch included in each of said low, middle and overdrive gear connections.

l0. An automatic, multiple speed transmission of the character disclosed comprising an input shaft, 'an output shaft, a countershaft, low, middle and overdrive gear connections from said input shaft to said countershaft, a clutch for each of said low,rniddle and overdrive gear y connections, a clutch for direct drive from s'aid input shaft to said output shaft, means to control said clutches for said low, middle and overdrive gear connections and said clutch for direct drive, an overrun clutch included in each of said low, middle and overdrive gear connections, a free-wheeling prevention clutch included in each of said low, middle 'and overdrive gear connections, said interconnected means to control said clutches for said low, middle and overdrive gear connections and said clutch for direct drive, said interconnected means also controlling said free-wheeling prevention clutches to render them progressively inoperative during 11p-shifting of said transmission.

11. An automatic, multiple speed transmission of the character disclosed comprising an input shaft, an output shaft, a countershaft, low, middle and overdrive gear connections from said input shaft to said countershaft, a clutch for each of said low, middle and overdrive gear connections, a clutch for direct drive from said input shaft to said output shaft, means to control said clutches f-or said low, middle and overdrive gear connections and said clutch for direct drive, an overrun clutch included in each of said low, middle and overdrive gear connections, a free-wheeling prevention clutch included in each of said low, middle and overdrive gear connections, said means to control said clutches for said gear connections and said clutch for direct drive also controlling said free-wheeling prevention clutches to render them progressively inoperative during up-shifting of said transmission and to se'- lectively render all of said free-wheeling clutches inoperative.

12. In a transmission of the character disclosed, an input shaft, an output shaft, a countershaft, low, middle and overdrive gear connections from said input shaft to said countershaft, a clutch for each of said gear connections, a clutch for direct drive from said input shaft t-o said output shaft, means to control said clutches for said low, middle and overdrive gear connections and said clutch for direct drive, an overrun clutch included in each of said low, middle and overdrive gear connections to permit progressive upeshifting and down-shifting of said transmission without declutching said output shaft relative to said input shaft, a plurality of gear connections between said countershaft and said output shaft, means for shifting said last gear connections to different ranges of relative speeds in the same direction between said two shafts, a free-wheeling prevention clutch included in each of said low, middle and overdrive plurality of gear connections, said means to control said clutches for said low, middle and overdrive gear connections and said clutch for direct drive also contnolliug Isaid free-wheeling prevention clutches to render them progressively inoperative during up-shifting of said transmission and to selectively render all of said free-wheeling clutches inoperative.

13. In a power transmission of the character disclosed, an input shaft, anoutput shaft, a countershaft, low, middle and overdrive gear connections from said input `shaft to said countershaft, a clutch for each of said low, middle and overdrive gear connections, a clutch for direct `drive from saidinput shaft to said output shaft, means to control said clutches for -said gear connections and said clutch for direct drive, an overrun clutch included in eachof said low, middle and overdrive gear connections to permit progressive up-shifting and down-shifting of said transmission without declutching said output shaft relative to said input shaft, a plurality of gear connections between said countershaft and said output shaft, means for Vshifting said last gear connections to different ranges of relative speeds in the same direction, and a freewheeling prevention clutch included in each of said low, middle and overdrive gear connections, said means to control said clutches for said low, middle and overdrive gear connections and said clutch for direct drive also controlling said free-wheeling prevention clutches to render them progressively inoperative during tip-shifting of said transmission.

14. In a power transmission of the character disclosed, an input shaft, an output shaft, a countershaft, low, middle and overdrive gear connections from said input shaft to said countershaft, a clutch for each of said low, middle and overdrive gear connections, a clutch for direct drive from said input shaft to said output shaft, means to control said clutches for said gear connections and said clutch for direct drive, a plurality of gear connections between said countershaft and said output shaft, means for shifting said last gear connections to diierent ranges of relative speeds in the same direction, and a free-wheeling prevention clutch included in each of said first connections, said means to control said clutches for said low, middle and overdrive gear connections and said clutch for direct drive also controlling said free-wheeling prevention clutches to render them progressively inoperative during up-shifting of said transmission.

15. In a transmission of the character disclosed, an input shaft, an output shaft, a countershaft, low, middle and overdrive gear connections from said input shaft to said countershaft, a clutch for each of said low, middle and overdrive gear connections, means to control said clutches for said low, middle and overdrive gear connections, an overrun clutch included in each of said low, middle and overdrive gear connections to permit progressive up-shifting and down-shifting of said transmission without declutching, a reverse gear connection between said input shaft and said countershaft, and interconnected means operable to selectively render one of said low,

middle and overdrive gear connections inoperative and 'Ell and overdrivelgear .connections from :said .input .shaft to said countershaft; .a :clutch for each of .said low, middle and overdrive gear connections, 'means to control said clutches'for said low, middle and #overdrive gear connections, an overrun clutch included in each of .said 10W, middlerand loverdrive gearconnections to .permit progressive up-shifting and down-shifting of said transmission without declutching, a plurality -of gear .connections between said countershaft and said output shaft, means :for

shifting .said last gear connections to dierent ranges of 10 2,394,580

relative speeds in the same direction between said two nectionsrinoperative and said reverse gear connection 5 operative or vice versa.

References Cited in the le of this .patent UNITED STATES PATENTS Banker Feb. 12, 1946 2,466,318 Kohr Apr. 5, 1949 

